Classifications

• • E—FIXED CONSTRUCTIONS
  • E04—BUILDING
  • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
  • E04H5/00—Buildings or groups of buildings for industrial or agricultural purposes
  • E04H5/02—Buildings or groups of buildings for industrial purposes, e.g. for power-plants or factories
• • E—FIXED CONSTRUCTIONS
  • E04—BUILDING
  • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
  • E04H5/00—Buildings or groups of buildings for industrial or agricultural purposes
  • E04H5/10—Buildings forming part of cooling plants
• • E—FIXED CONSTRUCTIONS
  • E04—BUILDING
  • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
  • E04H5/00—Buildings or groups of buildings for industrial or agricultural purposes
  • E04H5/10—Buildings forming part of cooling plants
  • E04H5/12—Cooling towers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K13/00—General layout or general methods of operation of complete plants
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
  • F02B43/10—Engines or plants characterised by use of other specific gases, e.g. acetylene, oxyhydrogen
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B65/00—Adaptations of engines for special uses not provided for in groups F02B61/00 or F02B63/00; Combinations of engines with other devices, e.g. with non-driven apparatus
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
  • F02D19/0639—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels
  • F02D19/0642—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions
  • F02D19/0647—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions the gaseous fuel being liquefied petroleum gas [LPG], liquefied natural gas [LNG], compressed natural gas [CNG] or dimethyl ether [DME]
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B27/00—Machines, plants or systems, using particular sources of energy
  • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
• • E—FIXED CONSTRUCTIONS
  • E04—BUILDING
  • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
  • E04H5/00—Buildings or groups of buildings for industrial or agricultural purposes
  • E04H2005/005—Buildings for data processing centers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
  • F02B43/10—Engines or plants characterised by use of other specific gases, e.g. acetylene, oxyhydrogen
  • F02B2043/103—Natural gas, e.g. methane or LNG used as a fuel
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2500/00—Problems to be solved
  • F25B2500/12—Sound
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
  • Y02A30/00—Adapting or protecting infrastructure or their operation
  • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
  • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E20/00—Combustion technologies with mitigation potential
  • Y02E20/14—Combined heat and power generation [CHP]

Definitions

• the present invention relates to a cogeneration plant.
• the invention relates to a cogeneration plant suitable for, but not limited to the powering and cooling of a data centre and will be described in this context.
• Data centres typically utilize more energy than typical commercial buildings, as they require proper cooling facilities to maintain the servers and electrical components. These servers and electrical components ideally should run at twenty-four hours, seven days a week (i.e. 24/7) barring scheduled downtimes and as such, a cogeneration configuration, i.e. production of two forms of usable energy from one fuel source, is a suitable and viable option to power and cool data centres efficiently.
• a common cogeneration configuration for data centres would be a gas- powered turbine/engine generator that generates electricity and heat. The electricity powers the equipment and the resulting heat (in the form of flue, hot water etc.) recovered from the turbine generator is then used to run one or more absorption chiller(s) to provide cooling via air-conditioning to the servers and electrical components, for example.
• Such a configuration where a cogeneration plant produces electricity energy, heat energy, and energy used for cooling simultaneously, is known as tri-generation.
• the present invention seeks to provide a cogeneration plant that alleviates the physical space constraint while meeting standard requirements at least in part.
• cogeneration plant refers to a plant producing electricity and heat which includes (but is not limited to) a tri- generation plant, where a cogeneration plant produces three types of energy including electricity, heat and energy used for cooling.
• a cogeneration plant unit comprising a base storey for housing a power generation source; a second storey vertically arranged above the base storey for housing an absorption chiller, the absorption chiller operable to be in fluid communication with the power generation source; a third storey vertically arranged above the second storey, the third storey for housing a cooling tower; and a chimney arranged in fluid communication with the power generation source and absorption chiller to dissipate the exhaust of the power generation source and the absorption chiller in operation.
• the cogeneration plant unit comprises at least one additional storey vertically arranged above the second storey, each of the at least one additional storey for housing an absorption chiller.
• the cogeneration plant unit comprises a muffler disposed between the base storey and the second storey for housing the absorption chiller(s).
• the cogeneration plant unit comprises at least one additional storey arranged between the storeys for housing absorption chillers and the third storey, the at least one additional storey for housing electrical components.
• the power generation source is a dual-fuel reciprocating (piston) engine operable in a mode driven by a combination of natural gas and diesel.
• the combination of natural gas and diesel comprises at least 90% natural gas.
• the combination of natural gas and diesel is utilized for a pilot-ignition of the power generation source, and thereafter natural gas is utilized as the single fuel for power generation.
• the absorption chiller is activated by an input of exhaust (flue gas), and supplemented by hot water.
• each power generation source is a reciprocating (piston) engine having a maximum load capacity of 8.7 megawatts and operable to produce an output at 50% load.
• each absorption chiller operates to produce 500 refrigeration tons.
• twelve of the twenty-four absorption chillers are operable each to produce 1000 refrigeration tons and the remaining twelve absorption chillers are not in operation or in stand-by mode.
• Fig. 1 is a schematic diagram of a cogeneration plant unit in accordance with an embodiment of the invention
• Fig. 2 is a schematic diagram of a cogeneration plant unit in accordance with another embodiment of the invention.
• Fig. 3 shows a possible operating arrangement having two of the cogeneration units of Fig. 2;
• Fig. 4 is a diagram of another embodiment of a cogeneration plant suited for use to power and cool a data centre, the cogeneration plant comprising twelve power generation sources coupled with twenty-four absorption chillers.
• the cogeneration plant comprising twelve power generation sources coupled with twenty-four absorption chillers.
• the cogeneration plant unit 10 comprises three storeys.
• cogeneration plant unit 10 comprises a base storey housing a power generation source 20; a second storey vertically arranged above the base storey for housing an absorption chiller 30, the absorption chiller 30 operable to be in fluid communication with the power generation source 20; a third storey vertically arranged above the second storey for housing cooling towers 50; and
• a chimney 60 arranged in fluid communication with the power generation source 20 and absorption chiller 30 to dissipate the exhaust of the absorption chiller 30 and the power generation source 20.
• One or more muffler(s) 70 may be suitably located (for example between the base and second storeys) to reduce the noise level generated by the power generation source 20.
• the power generation source 20 may also be housed in an enclosed area (not shown) to further reduce noise and/or protect the power generation source 20 against weather elements.
• the power generator 20 is preferably a reciprocating (piston) engine.
• Reciprocating (piston) engine 20 is a dual-fuel engine capable of being driven in various modes corresponding to the usage of two different types of fuel.
• the two different types of fuel are typically diesel and natural gas.
• power generator 20 is driven by a combination of primarily natural gas and a relatively small amount of diesel.
• the combination comprises at least 90% of natural gas.
• Natural gas is deemed to be a preferred fuel over diesel because the exhaust generated is cleaner and hence better for use as input for the absorption chiller 30.
• Each reciprocating engine 20 is configured to have a net electrical output depending on the needs of the application.
• the reciprocating engine 20 is operable to be in fluid communication, and/or coupled with the absorption chiller 30.
• the absorption chiller 30 is operably configured to be activated primarily based on exhaust (flue gas) fired, and supplemented by hot water.
• the absorption chiller 30 has an operating refrigerating capacity of up to 1000 USRT (refrigeration ton).
• the power generator 20 and absorption chiller 30 are connected via exhaust ducting configuration 80.
• the exhaust ducting configuration 80 comprises a first duct 82, a second duct 84 and a third duct 86 arranged in the following manner: -
• the first duct 82 is operable to connect exhaust from the reciprocating engine 20 to the chimney 60.
• the first duct 82 comprises two ends. One end of the first duct 82 is connected to the reciprocating engine 20 and the other end of the first duct 82 is connected to the chimney 60.
• the second duct 84 is operable to divert flue exhaust from the reciprocating engine 20 to the absorption chiller 30 for driving the absorption chiller 30.
• the second duct 84 comprises a first and a second part, the first part extending from a portion of the first duct 82 at one end and into the input (for flue exhaust) mechanism of the absorption chiller 30 at the other end; and the second part of the second duct 84 is jointed to the first part at one end and connected to the chimney 60 at the other end.
• the third duct 86 connects the exhaust of the absorption chiller 30 to the chimney 60 for dissipation.
• Valves 88 are located in suitable positions to direct/restrict the flow of fluid (including exhaust) in the first, second and third ducts 82, 84, 86 respectively.
• a valve 88 is positioned in the first duct 82 to direct the exhaust between reciprocating engine 20 to the chimney 60; or from the reciprocating engine 20 to the absorption chiller(s) 30.
• Additional valves 88 may be positioned in the second duct 84 to direct/restrict the flow of exhaust flue gas into the absorption chiller(s) 30.
• chimney 60 refers to any structure capable of providing ventilation for exhaust flue gas/smoke from the reciprocating engine(s) 20, absorption chiller(s) 30 to the outside surrounding or atmosphere. It may be made of different materials; for example bricks, metal etc. as long as the chimney 60 performs its desired function.
• a portion of the exhaust ducting configuration 80 may be housed in one or more additional storey(s) between the second and third storey housing cooling towers, if required.
• flue exhaust from the reciprocating engine 20 is input into the absorption chiller 30 through the exhaust ducting configuration 80 via the valves 88.
• Any excess exhaust from the reciprocating engine 20 not directed into the absorption chiller 30 is directed to the chimney 60 having about 60 metres stack height (flue-gas stack) through the first duct 82.
• the stack height of the chimney 60 is determined depending on laws/regulation in different jurisdictions. For example, under Singapore's regulation, the stack height is required as a minimum of three metres above the highest point in the installed building or a minimum of three metres above the highest point corresponding to a highest building within a 100 metres radius, whichever is higher.
• each reciprocating engine 20 in addition to flue exhaust, high temperature water (utilized for cooling) may be directed through a heat exchanger to the absorption chiller 30 (hot water module). Together with the flue exhaust and hot water as inputs to the absorption chiller 30, bulk of the one thousand (1000) refrigeration tons for the absorption chiller 30 is produced. In circumstances where the exhaust and hot water are insufficient, each absorption chiller 30 may further be equipped with a direct fired (dual fuel) burner. Alternatively, instead of a fuel combination of natural gas and diesel, the reciprocating engine 20 may be configured to operate using a full diesel mode, that is, using diesel as the only source of fuel.
• the exhaust flue will have to exhaust directly through its exhaust stack (via duct 82) to the chimney 60 as it is not suitable for use to drive the absorption chiller 30.
• the reciprocating engine 20 provides hot water to the absorption chiller 30 but the balance cooling capacity will have to be made up by the absorption chiller's 30 own burners in full diesel mode.
• the reciprocating engine 20 in full diesel mode is configured to be on a standby basis if natural gas is being disrupted. For example, if there is a natural gas feeding interruption. It is more economical and advantageous to operate with a combination of natural gas and diesel in terms of fuel and storage cost.
• the reciprocating engine 20 may be configured to operate only in natural gas mode, that is, using natural gas as the only source of fuel.
• the exhaust flue from the full natural gas mode is most suitable for feeding into most, if not all absorption chillers 30.
• the dual fuel mode or bi-fuel mode operation comprises blending diesel fuel and natural gas in a combustion chamber of the reciprocating engine 20.
• the blend may be achieved by using a pilot-ignition, fumigated gas-charge design, whereby natural gas is pre-mixed with intake air of the reciprocating engine 20 and delivered to the combustion chamber via one or more air-intake valves.
• the pilot ignition mode is used to start the reciprocating engine 20; after which the bi-fuel mode is switched to a full natural gas mode (i.e. 100% natural gas operation).
• a switch from dual fuel/ bi-fuel mode in the starting or initial stage to a single fuel (i.e. natural gas) mode after pilot-ignition achieves a desired level of cost efficiency in the ignition stage as natural gas generally costs more than diesel.
• cogeneration plant unit 100 comprises seven storeys.
• cogeneration plant unit 100 comprises a base storey housing power generation source 20; two storeys (3 rd and 4 th storeys) vertically arranged above the base storey; the two storeys (3 rd and 4 th ) for housing absorption chillers 30, the absorption chillers 30 operable to be in fluid communication with the power generation source 20; a storey (7 th storey) vertically arranged above of the 3 rd and 4 th storeys for housing cooling towers 50; and
• a chimney 60 arranged in fluid communication with the absorption chillers 30 to dissipate the exhaust of the absorption chillers and the power generation source 20.
• the 2 nd storey comprises one or more muffler(s) 70 to reduce the noise level generated by the power generation source 20.
• the power generation source comprises one or more muffler(s) 70 to reduce the noise level generated by the power generation source 20.
• 20 may also be housed in an enclosed area (not shown) to further reduce noise and/or protect the power generation source against weather elements.
• the base storey is therefore at least partially enclosed.
• the power generator 20 is a reciprocating (piston) engine.
• the reciprocating (piston) engine 20 may be driven in various modes corresponding to the usage of different types of fuel, such as diesel and/or natural gas.
• power generator 20 is a dual-fuel engine to be driven by a combination comprising primarily natural gas and a relatively small amount of diesel. Natural gas is deemed to be a preferred fuel over diesel because the exhaust generated is cleaner and hence better for use as input for the absorption chillers 30.
• the combination of fuel comprises at least 90% of natural gas.
• Each reciprocating engine 20 is configured to have a net electrical output depending on the needs of the application.
• the reciprocating engine 20 is operable to be in fluid communication, and/or coupled with the two units of absorption chillers 30 for the transmission of exhaust flue gas from the reciprocating engine 20 to the absorption chillers 30.
• Each absorption chiller 30 is operably configured to be activated primarily by exhaust (flue gas), and supplementary activated by hot water.
• Each absorption chiller 30 has an operating refrigerating capacity of up to 1000 USRT (refrigeration ton).
• the power generator 20 and absorption chillers 30 are connected via exhaust ducting configuration 80.
• the exhaust ducting configuration 80 described in the earlier embodiment may be extended for two absorption chillers.
• the exhaust ducting configuration 80 comprises a first duct 82 connected to the reciprocating engine 20 at one end and to the chimney 60 at the other end.
• the second ducts 84 instead of a single second duct 84, there are two second ducts 84, each comprising two parts, the first part extending from the first duct 82 at one end and into the input (for flue exhaust) of the absorption chiller 30; and the second part of the second duct 84 is jointed to the first part and connected to the chimney 60.
• Two third ducts 86 connect the exhaust of each of the absorption chillers 30 to the chimney 60 for dissipation.
• the efficiency measured via coefficient of performance (COP) of an absorption chiller 30 at 50 % load is 4% more than at full load efficiency.
• the COP increases from 0.77 to 0.8.
• Additional valves 88 may be positioned in the second duct 84 to direct/restrict the flow of exhaust flue gas into the absorption chiller(s) 30.
• chimney 60 refers to any structure capable of providing ventilation for exhaust flue gas/smoke from the reciprocating engine(s) 20, absorption chiller(s) 30 to the outside atmosphere. It may be made of different materials; for example bricks, metal etc. as long as it performs its desired function.
• flue exhaust from the reciprocating engine 20 is input into two absorption chillers 30 situated in level 3 and level 4 through the exhaust ducting configuration 80 via the valves 88. Any excess exhaust from the reciprocating engine 20 not exhausted into the absorption chillers 30 is directed to the chimney 60 having about 60 metres stack height (flue-gas stack).
• the stack height is determined depending on laws/regulation in different jurisdictions. For example, under Singapore's regulation, the stack height is required as a minimum of three metres above the highest point in the installed building or a minimum of three metres above the highest point corresponding to a highest building within a 100 metres radius, whichever is higher.
• each chiller may further be equipped with a direct fired (dual fuel) burner.
• the reciprocating engine 20 may be configured to operate only in diesel mode (100%). In such case, the exhaust flue will have to exhaust directly through its exhaust stack as it is not suitable for use to drive the absorption chillers 30. In the diesel mode operation, the reciprocating engine 20 still provides the hot water to the chillers but the balance cooling capacity have to be made up by the absorption chillers 30 own burners in diesel mode. It is to be appreciated that the reciprocating engine in full diesel mode is configured to be on a standby basis if natural gas is being disrupted. It is more economical and advantageous to operate in natural gas mode than in diesel mode in terms of fuel and storage cost.
• the reciprocating engine 20 may be configured to operate only in natural gas mode.
• the dual fuel mode or bi-fuel mode operation comprises blending diesel fuel and natural gas in a combustion chamber of the reciprocating engine 20.
• the blend may be achieved by using a pilot-ignition, fumigated gas-charge design, whereby natural gas is pre-mixed with intake air of the reciprocating engine 20 and delivered to the combustion chamber via one or more air-intake valves.
• the pilot ignition mode is used to start the reciprocating engine 20; after which the bi-fuel mode is switched to a full natural gas mode (i.e. 100% natural gas operation).
• a switch from dual fuel/ bi-fuel mode in the starting or initial stage to a single fuel (i.e. natural gas) mode after pilot-ignition achieves a desired level of cost efficiency in the ignition stage as natural gas generally costs more than diesel.
• the described cogeneration plant unit 100 in Fig. 2 having seven storeys is viewed as a basic configuration.
• the basic configuration described is extended to comprise six power generators 20 and twelve absorption chillers 30.
• the six reciprocating engines 20 are configured to produce a total of about 52 megawatts of electrical energy, and the absorption chillers about 12,000 Refrigeration tons (1000 Rtons x 2 units per set x 6 sets per module) of chilled water cooling capacity at 7 degrees Celsius supply and 12 degrees Celsius return.
• the described cogeneration plant unit 100 is viewed as a basic configuration.
• the described basic configuration is extended to comprise twelve units of dual fired engine generators 20 and twenty-four units of absorption chillers 30 as illustrated in Fig. 4.
• each of the engine generators 20 operates at 50% load based on an example of 8.7 megawatts at 100% load, i.e. at 4.35 megawatts.
• twelve units of the dual fired engine generators 20 would produce approximately 52 Mega Watts load.
• each absorption chiller 30 may be configured to operate at 500 Refrigeration tons, thus producing a total of 12,000 Refrigeration tons.
• each engine exhaust and hot water from an engine generator 20 could be directed into one absorption chiller instead of two. At any one operating period, one absorption chiller is thus produce 1 ,000 Refrigeration tons.
• the other absorption chiller 30 functions as a form of back-up (providing redundancy) in case the operating absorption chiller 30 breaks down.
• Reliability analysis had been carried out on the described data centre 400, in particular on the reliability of one unit of generator 20 coupled with two units of absorption chillers 30.
• the reliability analysis is based on the assumption that the reliability of the generator 20 RG is 0.9 and the reliability for each absorption chiller Rgb is 0.8.
• R (unit) R G x ⁇ 1- (1- Rab)(1- Rab) ⁇
• the reliability of the system would be calculated based on the following probabilities:- Event A corresponding to all twelve generator units 20 in operation + Event B as 1 1 generator units run and one unit fails.
• At least one of the eleven running units will be necessary for the increase from a 50% to 100% loading operation.
• the cogeneration plant unit 10 may be implemented in areas where land are scarce (e.g. Singapore), while providing reliable requirements meeting Tier 4 of the Uptime Institute certification.
• the described embodiment also makes use of the thermodynamic concept of 'hot air rises cool air sinks' by having the absorption chillers 30 positioned above of the engine 20, so the hot flue exhaust of the engine 20 rises to power the absorption chillers 30 via the exhaust ducting configuration 80.
• the adaption of the basic vertical configuration to power a data centre at a 50% load as described in the above embodiment is advantageous to meet the requirements for Tier 4 certification of the Uptime Institute and achieve physical space savings.
• the reciprocating piston engine 20 is heavy and requires preferably an independent structural support when the plant 10, 400 is built.
• the independent structural support is separated from the rest of the building so that vibrations resulting from the operation of the reciprocating piston engines 20 are isolated from the rest of the plant.
• Additional generators 20 and/or absorption chillers 30 may be added into the embodiments for redundancy.
• references to the terms 'base', 'first', 'second', 'third', 'fourth', 'fifth', storeys etc. in the described embodiments are terms used in the context for illustrating the order of the various elements housed within the cogeneration plant unit/plant.
• the reference is by no means restrictive and additional storeys may be added between the storeys as known by a person skilled in the art.
• one or more storeys housing similar items may be combined into a single storey having a higher height than other storeys as required to meet height, regulatory or other requirements.

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• Engineering & Computer Science (AREA)
• Architecture (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Civil Engineering (AREA)
• Structural Engineering (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Oil, Petroleum & Natural Gas (AREA)
• Sorption Type Refrigeration Machines (AREA)

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• 2013
  • 2013-12-26 SG SG2013095864A patent/SG2013095864A/en unknown
• 2014
  • 2014-12-23 US US15/108,309 patent/US20160319560A1/en not_active Abandoned
  • 2014-12-23 CN CN201480076413.6A patent/CN107075975A/zh active Pending
  • 2014-12-23 EP EP14873831.3A patent/EP3097278A4/de not_active Withdrawn
  • 2014-12-23 SG SG11201605225SA patent/SG11201605225SA/en unknown
  • 2014-12-23 WO PCT/SG2014/000611 patent/WO2015099611A1/en active Application Filing

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